JPH04296251A - Shift controller for friction roller type continuously variable transmission - Google Patents
Shift controller for friction roller type continuously variable transmissionInfo
- Publication number
- JPH04296251A JPH04296251A JP3087821A JP8782191A JPH04296251A JP H04296251 A JPH04296251 A JP H04296251A JP 3087821 A JP3087821 A JP 3087821A JP 8782191 A JP8782191 A JP 8782191A JP H04296251 A JPH04296251 A JP H04296251A
- Authority
- JP
- Japan
- Prior art keywords
- spool
- sleeve
- axial direction
- step motor
- rotating shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 22
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 239000003921 oil Substances 0.000 description 41
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
- F16H2015/383—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces with two or more sets of toroid gearings arranged in parallel
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
Description
【０００１】0001
【産業上の利用分野】本発明は、摩擦車式無段変速機の
変速制御装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change control device for a friction wheel type continuously variable transmission.
【０００２】0002
【従来の技術】摩擦車式無段変速機の変速制御装置とし
て、本出願人が先に出願した特願平２−１３１９４５号
に示されるものがある。これに示される変速制御装置の
変速制御弁は、指令される変速比に応じて回転位置が決
定されるステップモータと、ステップモータによって軸
方向に移動可能なスリーブと、スリーブの内径にはめ合
わされるスプールなどを有している。スプールはカム、
リンクなどを介して実際の変速比に対応するように軸方
向に駆動される。ステップモータに指令される変速比と
実際の変速比とが対応した状態でスリーブとスプールと
の相対位置関係は基準状態となって油圧シリンダ装置に
はこの時点の変速比を維持するように油圧が供給される
。一方、スリーブとスプールとが上記基準状態からずれ
た場合には、油圧シリンダ装置には実際の変速比が指令
される変速比に対応するものとなるように油圧が供給さ
れる。2. Description of the Related Art A speed change control device for a friction wheel type continuously variable transmission is disclosed in Japanese Patent Application No. 2-131945 filed earlier by the present applicant. The speed change control valve of the speed change control device shown in this figure includes a step motor whose rotational position is determined according to a commanded speed ratio, a sleeve movable in the axial direction by the step motor, and a sleeve that is fitted into the inner diameter of the sleeve. It has a spool etc. The spool is a cam,
It is driven in the axial direction via a link or the like to correspond to the actual gear ratio. When the gear ratio commanded to the step motor corresponds to the actual gear ratio, the relative positional relationship between the sleeve and the spool becomes the reference state, and the hydraulic cylinder device receives hydraulic pressure to maintain the gear ratio at this point. Supplied. On the other hand, if the sleeve and spool deviate from the reference state, hydraulic pressure is supplied to the hydraulic cylinder device so that the actual gear ratio corresponds to the commanded gear ratio.
【０００３】0003
【発明が解決しようとする課題】しかしながら、上記摩
擦車式無段変速機の変速制御装置には、スリーブを移動
させる際に摩擦抵抗がこれの外周及び内周の両方で発生
するため、スリーブを動かすための作動力が大きくなる
という問題がある。特に極低温時には作動油の粘度が増
加するため、この問題が顕著となる。したがって、スリ
ーブを移動させるステップモータの駆動力が大きくなる
ため、モータを大きくする必要がある。本発明はこのよ
うな課題を解決することを目的としている。[Problems to be Solved by the Invention] However, in the speed change control device of the friction wheel type continuously variable transmission, frictional resistance is generated on both the outer circumference and the inner circumference of the sleeve when the sleeve is moved. There is a problem in that the actuation force required for movement becomes large. This problem becomes particularly pronounced at extremely low temperatures because the viscosity of the hydraulic oil increases. Therefore, the driving force of the step motor that moves the sleeve becomes large, so it is necessary to make the motor larger. The present invention aims to solve these problems.
【０００４】0004
【課題を解決するための手段】本発明は、変速制御弁の
スリーブの内径部にはめ合わされるスプールをステップ
モータによって駆動し、スリーブを実際の変速比に対応
するように駆動することによって、上記課題を解決する
。すなわち、本発明は、入力ディスク（２６、３２）と
、出力ディスク（２８、３４）と、両ディスクによって
形成されるトロイド状のみぞ内に両ディスクと摩擦接触
するように配置される摩擦ローラ（３０、３２）と、摩
擦ローラを偏心軸（８４）を介して回転自在に支持する
とともに両ディスクの軸心に直交する回転軸部（８３ａ
、８３ｂ）を中心として回動可能かつ上記回転軸部の軸
方向に移動可能なローラ支持部材（８３）と、ローラ支
持部材を上記回転軸部の軸方向に駆動可能な油圧シリン
ダ装置（３０４、１２４）と、を有する摩擦車式無段変
速機の変速制御装置において、油圧シリンダ装置の油圧
を制御する変速制御弁（４１０）と、ローラ支持部材に
これと一体に回転するように取り付けられる斜面カム（
３２０）と、カムの斜面に一端が接触して設けられると
ともにカムの回転により揺動可能なリンク（３２２）と
、を有しており、変速制御弁は互いに相対移動可能な状
態にはまり合ったスリーブ（４１８）及びスプール（４
１６）と、指令される変速比に応じて回転位置が決定さ
れるステップモータ（４１２）と、ステップモータによ
って軸方向に駆動される駆動部材（４１４）と、を有し
ており、スプールは駆動部材と軸方向に一体に移動する
ように連結され、スリーブは上記回転軸部の回転変位に
応じて軸方向に移動するように上記リンクの他端と連結
され、スリーブ及びスプールは指令される変速比と上記
回転軸部の回転変位とが対応した状態で両者との相対位
置関係が基準状態となって油圧シリンダ装置へ供給する
油圧をこれが上記回転軸部の回転変位を維持するように
上記回転軸部に軸方向の一定の力を作用するように調整
し、スリーブとスプールとが上記基準状態からずれた場
合には油圧シリンダ装置へ供給する油圧をこれが上記回
転軸部の回転変位が指令される変速比に対応するものと
なるように上記回転軸部に軸方向に作用する力を変化さ
せるように調整する構成とされていることを特徴とする
。なお、上述のかっこ内の数字は後述の実施例の対応す
る部材の符号である。[Means for Solving the Problems] The present invention provides the above-mentioned method by driving a spool fitted to the inner diameter part of a sleeve of a speed change control valve using a step motor, and driving the sleeve to correspond to an actual speed change ratio. solve problems. That is, the present invention provides an input disk (26, 32), an output disk (28, 34), and a friction roller () disposed in a toroidal groove formed by both disks so as to be in frictional contact with both disks. 30, 32), and a rotating shaft portion (83a) that rotatably supports the friction roller via an eccentric shaft (84) and is orthogonal to the axes of both disks.
, 83b) and movable in the axial direction of the rotating shaft; and a hydraulic cylinder device (304, 304) capable of driving the roller supporting member in the axial direction of the rotating shaft. 124) A speed change control device for a friction wheel type continuously variable transmission comprising: a speed change control valve (410) for controlling oil pressure of a hydraulic cylinder device; and a slope surface attached to a roller support member so as to rotate together with the speed change control valve (410). cam(
320) and a link (322) which is provided with one end in contact with the slope of the cam and is swingable by the rotation of the cam, and the speed change control valves are fitted in a state in which they can move relative to each other. Sleeve (418) and spool (4
16), a step motor (412) whose rotational position is determined according to a commanded gear ratio, and a drive member (414) that is driven in the axial direction by the step motor, and the spool is driven The sleeve is connected to the other end of the link so as to move in the axial direction in accordance with the rotational displacement of the rotating shaft portion, and the sleeve and spool are connected to a commanded speed change. When the ratio corresponds to the rotational displacement of the rotating shaft, the relative positional relationship between the two becomes a reference state, and the hydraulic pressure supplied to the hydraulic cylinder device is adjusted to maintain the rotational displacement of the rotating shaft. Adjustment is made so that a constant force in the axial direction is applied to the shaft, and when the sleeve and spool deviate from the above-mentioned reference state, the hydraulic pressure supplied to the hydraulic cylinder device is controlled so that the rotational displacement of the rotary shaft is commanded. The present invention is characterized in that it is configured to adjust the force acting on the rotating shaft portion in the axial direction so as to correspond to the speed change ratio. Note that the numbers in parentheses above are the codes of corresponding members in the embodiments described later.
【０００５】[0005]
【作用】スプールの摩擦抵抗は小径の外周にしか発生せ
ず、一方、スリーブの摩擦抵抗はこれの外周及び内周に
発生するので、スプールの摩擦抵抗はスリーブの摩擦抵
抗よりも小さい。摩擦抵抗の小さいスプールをステップ
モータで移動するため、ステップモータの駆動力は小さ
くてすみ、ステップモータを小型化することができる。[Operation] Frictional resistance of the spool occurs only on the outer periphery of the small diameter, while frictional resistance of the sleeve occurs on the outer and inner peripheries of the spool, so the frictional resistance of the spool is smaller than that of the sleeve. Since the spool with low frictional resistance is moved by the step motor, the driving force of the step motor is small, and the step motor can be made smaller.
【０００６】[0006]
【実施例】図１及び図２に実施例を示す。図１に示すよ
うに、ケーシング１０内に第１無段変速機構２２及び第
２無段変速機構２４が設けられている。第１無段変速機
構２２は、入力ディスク２６と、出力ディスク２８と、
両者間の回転力を伝達する一対の摩擦ローラ３０とを有
している。入力ディスク２６及び出力ディスク２８の摩
擦ローラ３０との接触面はトロイド面としてある。入力
ディスク２６及び出力ディスク２８に対する摩擦ローラ
３０の接触状態を変えることにより、入力ディスク２６
と出力ディスク２８との回転速度比を連続的に変えるこ
とができる。第２無段変速機構２４も、第１無段変速機
構２２と同様の入力ディスク３２と、出力ディスク３４
と、一対の摩擦ローラ３６とを有している。ただし、入
力ディスク３２及び出力ディスク３４の配置は、第１無
段変速機構２２とは逆としてある。すなわち、出力ディ
スク２８及び出力ディスク３４が互いに隣接するように
配置してある。入力ディスク２６は入力軸３８の外周に
ボールスプラインを介して支持されている。入力軸３８
は図示を省略した前後進切換機構及びトルクコンバータ
と連結されており、これらを介してエンジンの回転力が
入力されるように構成されている。入力ディスク２６の
背面側にカムフランジ４２が配置されている。カムフラ
ンジ４２及び入力ディスク２６の互いに対面するカム面
にカムローラ４６が設けられている。カムローラ４６は
入力ディスク２６とカムフランジ４２とが相対回転した
とき入力ディスク２６を出力ディスク２８側に押圧する
力を発生するような形状としてある。第２無段変速機構
２４の入力ディスク３２も入力軸３８にボールスプライ
ンを介して連結されている。入力ディスク３２は入力軸
３８にねじ込まれるローディングナット５０から圧縮力
を受けるディッシュプレート５１により出力ディスク３
４向きの力を受けている。第１無段変速機構２２の出力
ディスク２８及び第２無段変速機構２４の出力ディスク
３４はそれぞれニードルベアリングを介して入力軸３８
上に回転可能に支持されている。出力ディスク２８及び
出力ディスク３４と一体に回転するように駆動歯車５５
が設けられている。駆動歯車５５は入力軸３８と平行に
配置された中間軸５９の一端にスプラインによって一体
に回転するように結合された従動歯車６０とかみ合って
いる。中間軸５９の他端側に一体に形成された歯車６１
は、図示してないアイドラ歯車を介して、出力軸６２と
一体の歯車６３とかみ合っている。[Embodiment] An embodiment is shown in FIGS. 1 and 2. As shown in FIG. 1, a first continuously variable transmission mechanism 22 and a second continuously variable transmission mechanism 24 are provided within the casing 10. The first continuously variable transmission mechanism 22 includes an input disk 26, an output disk 28,
It has a pair of friction rollers 30 that transmit rotational force therebetween. The contact surfaces of the input disk 26 and the output disk 28 with the friction roller 30 are toroidal surfaces. By changing the contact state of the friction roller 30 with the input disk 26 and the output disk 28, the input disk 26
The rotational speed ratio between the output disk 28 and the output disk 28 can be continuously changed. The second continuously variable transmission mechanism 24 also includes an input disk 32 and an output disk 34 similar to the first continuously variable transmission mechanism 22.
and a pair of friction rollers 36. However, the arrangement of the input disk 32 and the output disk 34 is opposite to that of the first continuously variable transmission mechanism 22. That is, the output disk 28 and the output disk 34 are arranged adjacent to each other. The input disk 26 is supported on the outer periphery of the input shaft 38 via a ball spline. Input shaft 38
is connected to a forward/reverse switching mechanism and a torque converter (not shown), and is configured so that the rotational force of the engine is inputted via these. A cam flange 42 is arranged on the back side of the input disk 26. A cam roller 46 is provided on cam surfaces of the cam flange 42 and the input disk 26 that face each other. The cam roller 46 is shaped to generate a force that presses the input disk 26 toward the output disk 28 when the input disk 26 and cam flange 42 rotate relative to each other. The input disk 32 of the second continuously variable transmission mechanism 24 is also connected to the input shaft 38 via a ball spline. The input disk 32 is connected to the output disk 3 by a dish plate 51 that receives compressive force from a loading nut 50 screwed into the input shaft 38.
It is receiving forces in four directions. The output disk 28 of the first continuously variable transmission mechanism 22 and the output disk 34 of the second continuously variable transmission mechanism 24 are connected to the input shaft 38 via needle bearings, respectively.
It is rotatably supported on the top. A drive gear 55 is configured to rotate together with the output disks 28 and 34.
is provided. The driving gear 55 meshes with a driven gear 60 connected to one end of an intermediate shaft 59 disposed parallel to the input shaft 38 by a spline so as to rotate together. A gear 61 integrally formed on the other end side of the intermediate shaft 59
is meshed with a gear 63 integral with the output shaft 62 via an idler gear (not shown).
【０００７】図２に第１無段変速機構２２の部分の断面
図を示す（なお、第２無段変速機構２４についても基本
的な構成は図２に示す第１無段変速機構２２のものと同
一である）。ローラ支持部材８３は上下の回転軸部８３
ａ及び８３ｂにおいて球面軸受１１０及び１１２によっ
て回転可能かつ上下方向に移動可能に支持されている。
このローラ支持部材８３に偏心軸８４を介して前述の摩
擦ローラ３０が回転可能に支持されている。球面軸受１
１０はリンク１１４によって支持され、このリンク１１
４はケーシング１０に固着されたリンクポスト１１６に
よって支持されている。また、球面軸受１１２もリンク
１１８によって支持され、このリンク１１８はリンクポ
スト１２０によって支持されている。ローラ支持部材８
３は、回転軸部８３ｂと同心に設けられた延長軸部８３
ｃを有している。なお、延長軸部８３ｃは回転軸部８３
ｂと一体に回転するように構成されている。延長軸部８
３ｃの外周にピストン１２４が設けられている。ピスト
ン１２４はケーシング１０にボルト３００によって取り
つけられる主シリンダボディ３０２ａに形成されたピス
トン挿入穴３０４に挿入されている。なお、主シリンダ
ボディ３０２ａの下面はセパレートプレート３０６を介
して上述のボルト３００によって共締めされる副シリン
ダボディ３０２ｂが取りつけられており、これと主シリ
ンダボディ３０２ａとによってシリンダボディ３０２が
構成されている。これによってピストン１２４の上下に
油室１２８及び１３０（なお、図中右側と左側とでは油
室１２８と油室１３０とは上下逆となっている）が形成
されており、これに作用する油圧によりピストン１２４
は上下動可能である。ピストン１２４及び主シリンダボ
ディ３０２ａのピストン挿入穴３０４によって油圧シリ
ンダ装置が構成される。FIG. 2 shows a sectional view of a portion of the first continuously variable transmission mechanism 22 (the basic configuration of the second continuously variable transmission mechanism 24 is also that of the first continuously variable transmission mechanism 22 shown in FIG. 2). ). The roller support member 83 has upper and lower rotating shaft parts 83
a and 83b are rotatably and vertically movably supported by spherical bearings 110 and 112. The aforementioned friction roller 30 is rotatably supported by this roller support member 83 via an eccentric shaft 84 . Spherical bearing 1
10 is supported by a link 114, which link 11
4 is supported by a link post 116 fixed to the casing 10. The spherical bearing 112 is also supported by a link 118, which in turn is supported by a link post 120. Roller support member 8
3 is an extended shaft portion 83 provided concentrically with the rotating shaft portion 83b.
It has c. Note that the extended shaft portion 83c is the rotating shaft portion 83.
It is configured to rotate together with b. Extension shaft part 8
A piston 124 is provided on the outer periphery of 3c. The piston 124 is inserted into a piston insertion hole 304 formed in a main cylinder body 302a that is attached to the casing 10 by bolts 300. Note that a sub cylinder body 302b is attached to the lower surface of the main cylinder body 302a via a separate plate 306 and is fastened together with the above-mentioned bolts 300, and the cylinder body 302 is constituted by this and the main cylinder body 302a. . As a result, oil chambers 128 and 130 are formed above and below the piston 124 (the oil chambers 128 and 130 are upside down on the right and left sides of the figure), and the oil pressure acting on these piston 124
can move up and down. The piston 124 and the piston insertion hole 304 of the main cylinder body 302a constitute a hydraulic cylinder device.
【０００８】シリンダボディ３０２の下方にバルブボデ
ィ３１０が配置されている。バルブボディ３１０は、主
バルブボディ３１０ａと、これの上面にセパレートプレ
ート３１１を介して取り付けられる副バルブボディ３１
０ｂとから構成される。主バルブボディ３１０ａには変
速制御弁４１０が設けられる。変速制御弁４１０は、指
令される変速比に応じて回転駆動されるステップモータ
４１２と、ステップモータ４１２によって駆動されるピ
ニオン４１２ａとかみ合う歯が設けられるとともにステ
ップモータ４１２の回転によって軸方向に移動可能なラ
ック付きスプール４１４（駆動部材）と、一端がラック
付きスプール４１４と連結されており、ステップモータ
４１２の回転によってラック付きスプール４１４ととも
に軸方向に移動可能なスプール４１６と、スプール４１
６の外周に設けられるスリーブ４１８と、スリーブ４１
８を図中左方向に押圧するスプリング４１９と、スリー
ブ４１８の外側端部にはめ込まれるリテーナ４２０と、
を有している。主バルブボディ３１０ａには、油路４２
２及び油路４２４が設けられる。油路４２２は油室１２
８に接続される。また、油路４２４は油室１３０に接続
される。油路４２２及び油路４２４には、油路４２３の
ライン圧を油圧源として、スプール４１６及びスリーブ
４１８の相対位置関係に応じて油圧が配分される。すな
わち、スプール４１６のランドとスリーブ４１８の油み
ぞとの関係は、図２に示す基準状態では油路４２２及び
油路４２４の油圧を等しくし、スプール４１６が相対的
に左に移動した場合には油路４２４の油圧を油路４２２
の油圧よりも高くするように、またスプール４１６が相
対的に右に移動した場合には油路４２４の油圧を油路４
２２の油圧よりも低くするように、設定されている。延
長軸部８３ｃの下端にはこれと一体に回転可能なカム３
２０が設けられる。カム３２０は斜面を有しており、こ
れにリンク３２２が接触している。これによりカム３２
０が回転するとリンク３２２は揺動し、リンク３２２の
先端はリテーナ４２０を押圧可能である。A valve body 310 is arranged below the cylinder body 302. The valve body 310 includes a main valve body 310a and a sub-valve body 31 attached to the upper surface of the main valve body 310a via a separate plate 311.
0b. A speed change control valve 410 is provided in the main valve body 310a. The speed change control valve 410 is provided with a step motor 412 that is rotationally driven according to a commanded speed ratio, and teeth that mesh with a pinion 412a that is driven by the step motor 412, and is movable in the axial direction by the rotation of the step motor 412. a racked spool 414 (driving member), a spool 416 whose one end is connected to the racked spool 414 and is movable in the axial direction together with the racked spool 414 by rotation of the step motor 412;
A sleeve 418 provided on the outer periphery of 6 and a sleeve 41
8 to the left in the figure; a retainer 420 fitted into the outer end of the sleeve 418;
have. The main valve body 310a includes an oil passage 42.
2 and an oil passage 424 are provided. The oil passage 422 is the oil chamber 12
Connected to 8. Further, the oil passage 424 is connected to the oil chamber 130. Oil pressure is distributed to the oil passage 422 and the oil passage 424 according to the relative positional relationship between the spool 416 and the sleeve 418 using the line pressure of the oil passage 423 as a hydraulic pressure source. That is, the relationship between the land of the spool 416 and the oil groove of the sleeve 418 is such that in the standard state shown in FIG. The oil pressure in the oil passage 424 is transferred to the oil passage 422.
If the spool 416 moves relatively to the right, the oil pressure in the oil passage 424 is adjusted to be higher than the oil pressure in the oil passage 424.
It is set to be lower than the oil pressure of 22. A cam 3 that can rotate integrally with the lower end of the extended shaft portion 83c
20 are provided. The cam 320 has a slope, and the link 322 is in contact with the slope. As a result, the cam 32
0 rotates, the link 322 swings, and the tip of the link 322 can press the retainer 420.
【０００９】次にこの実施例の動作について説明する。
入力軸３８の回転が上昇すると、カムローラ４６の作用
により入力ディスク２６がカムフランジ４２に追従して
回転し、同時に入力軸３８の入力トルクに見合った推力
を発生させる。これにより摩擦ローラ３０は入力ディス
ク２６と出力ディスク２８とにはさみ付けられて滑るこ
となく回転し、入力ディスク２６から出力ディスク２８
への動力伝達が行われる。例えば変速比を大側に変える
場合には、ステップモータ４１２によってラック付きス
プール４１４を図中左方向へ移動させ、これによってス
プール４１６を図中左方向へ移動させる。スリーブ４１
８は直ちには移動しないのでスプール４１６とスリーブ
４１８との相対関係が変化し、油路４２４の油圧が上昇
し、油路４２２の油圧が低下する。油路４２２の油圧は
油室１２８に供給されており、また油路４２４の油圧は
油室１３０に供給されているので、図中右側のピストン
１２４はこれを上方向へ移動させようとする力を受ける
。一方、左側の油室１２８及び１３０については油室の
配置を右側とは上下を逆としてあるため、左側のピスト
ン１２４はこれを図中下方向に移動させようとする力を
受ける。これにより、右側のローラ支持部材８３は上向
きに移動しようとし、左側のローラ支持部材８３は下向
きに移動しようとする。これに伴って摩擦ローラ２２に
作用する接線方向の力の向きが変わるので、左右のロー
ラ支持部材８３はそれぞれ回転軸部８３ａ及び８３ｂを
中心として反対方向に回転する。これにより摩擦ローラ
３０の入力ディスク２６との接触位置半径は小さくなり
、逆に出力ディスク２８との接触位置半径は大きくなる
。すなわち、変速比は大側に変化する。ローラ支持部材
８３の回転は延長軸部８３ｃを介してカム３２０に伝達
され、更にカム３２０が回転するとリンク３２２が揺動
し、リンク３２２の先端は図中左方向へ移動する。これ
によりスプリング４１９によってスリーブ４１８は図中
左方向に移動する。スリーブ４１８が図中左方向に移動
するに従って油路４２２と油路４２４との油圧は同じ油
圧に近づき、最終的に油圧値が同じとなった基準状態で
安定する。Next, the operation of this embodiment will be explained. When the rotation of the input shaft 38 increases, the input disk 26 rotates following the cam flange 42 due to the action of the cam roller 46, and at the same time generates a thrust commensurate with the input torque of the input shaft 38. As a result, the friction roller 30 is sandwiched between the input disk 26 and the output disk 28 and rotates without slipping.
Power is transmitted to. For example, when changing the gear ratio to the larger side, the step motor 412 moves the racked spool 414 to the left in the figure, thereby moving the spool 416 to the left in the figure. Sleeve 41
8 does not move immediately, the relative relationship between the spool 416 and the sleeve 418 changes, the oil pressure in the oil passage 424 increases, and the oil pressure in the oil passage 422 decreases. The oil pressure in the oil passage 422 is supplied to the oil chamber 128, and the oil pressure in the oil passage 424 is supplied to the oil chamber 130, so the piston 124 on the right side of the figure has a force that tries to move it upward. receive. On the other hand, since the oil chambers 128 and 130 on the left side are arranged upside down from the right side, the piston 124 on the left side receives a force that tends to move it downward in the figure. As a result, the roller support member 83 on the right side tends to move upward, and the roller support member 83 on the left side tends to move downward. Accordingly, the direction of the tangential force acting on the friction roller 22 changes, so that the left and right roller support members 83 rotate in opposite directions about the rotating shafts 83a and 83b, respectively. As a result, the radius of the contact position of the friction roller 30 with the input disk 26 becomes smaller, and conversely the radius of the contact position with the output disk 28 becomes larger. That is, the gear ratio changes to the larger side. The rotation of the roller support member 83 is transmitted to the cam 320 via the extended shaft portion 83c, and when the cam 320 further rotates, the link 322 swings, and the tip of the link 322 moves to the left in the figure. As a result, the sleeve 418 is moved to the left in the figure by the spring 419. As the sleeve 418 moves leftward in the figure, the oil pressures in the oil passages 422 and 424 approach the same oil pressure, and eventually stabilize in the reference state where the oil pressure values are the same.
【００１０】変速比を小側に変更する場合、基本的な作
用は同様であるが、ステップモータ４１２の回転方向を
逆にするため、動作は上記動作と逆になる。したがって
、延長軸部８３ｃを介してカム３２０に伝達される回転
も逆になるため、リンク３２２の先端は図中右方向へ移
動し、リテーナ４２０を右方向へ押圧する。これにより
スリーブ４１８は図中右方向に移動して、油路４２２と
油路４２４との油圧値が同じとなった状態で安定する。
なお、上記説明は、第１無段変速機構２２について変速
作用を説明したが、第２無段変速機構２４についても同
様の作用が行われる。When changing the speed ratio to the smaller side, the basic operation is the same, but since the direction of rotation of the step motor 412 is reversed, the operation is opposite to the above operation. Therefore, the rotation transmitted to the cam 320 via the extended shaft portion 83c is also reversed, so the tip of the link 322 moves rightward in the figure and presses the retainer 420 rightward. As a result, the sleeve 418 moves rightward in the figure, and becomes stable in a state where the oil pressure values of the oil passage 422 and the oil passage 424 are the same. In addition, although the above description has explained the speed change operation for the first continuously variable transmission mechanism 22, the same operation is performed for the second continuously variable transmission mechanism 24 as well.
【００１１】上述のように、変速制御弁４１０のスプー
ル４１６がラック付きスプール４１４を介してステップ
モータ４１２によって駆動される。スプール４１６はこ
れの外径部においてスリーブ４１８の内径部にはめ合わ
されており、軸方向に移動した場合の摩擦抵抗はこのは
め合い部においてのみ発生する。一方、スリーブ４１８
はこれの内径部においてスプール４１６とはめ合わされ
ているのに加えて、外径部において主バルブボディ３１
０ａの穴にはめ合わされており、内外径の両方において
摩擦抵抗が発生する。したがって、スプール４１６を軸
方向に駆動するのに要する力は、スリーブ４１８を軸方
向に駆動するのに要する力よりも小さくなっている。し
たがって、スプール４１６を駆動するようにしたこの実
施例では、ステップモータ４１２を小型化することがで
きる。As mentioned above, the spool 416 of the speed change control valve 410 is driven by the step motor 412 via the racked spool 414. The outer diameter of the spool 416 is fitted into the inner diameter of the sleeve 418, and frictional resistance when moving in the axial direction occurs only at this fitted portion. On the other hand, sleeve 418
is fitted with the spool 416 at its inner diameter, and in addition, the main valve body 31 is fitted at its outer diameter.
It is fitted into the hole 0a, and frictional resistance is generated on both the inner and outer diameters. Therefore, the force required to drive spool 416 axially is less than the force required to drive sleeve 418 axially. Therefore, in this embodiment in which the spool 416 is driven, the step motor 412 can be downsized.
【００１２】0012
【発明の効果】以上説明してきたように、本発明による
と、スリーブよりも摩擦抵抗の小さいスプールをステッ
プモータで駆動するようにしたので、ステップモータの
駆動力が小さくてすみ、ステップモータを小型化するこ
とができる。また、ステップモータを小型化することに
よって駆動電力を少なくすることができる。[Effects of the Invention] As explained above, according to the present invention, the spool, which has lower frictional resistance than the sleeve, is driven by the step motor, so the driving force of the step motor can be small, and the step motor can be made smaller. can be converted into Further, by downsizing the step motor, driving power can be reduced.
【図１】本発明の実施例を示す図である。FIG. 1 is a diagram showing an embodiment of the present invention.
【図２】図１の２−２線に添う断面図である。FIG. 2 is a sectional view taken along line 2-2 in FIG. 1;
１０ ケーシング
２６ 入力ディスク
２８ 出力ディスク
３０ 摩擦ローラ
３２ 入力ディスク
３４ 出力ディスク
３６ 摩擦ローラ
８３ ローラ支持部材
１２４ ピストン
３２０ カム
３２２ リンク
４１０ 変速制御弁
４１２ ステップモータ
４１４ ラック付きスプール（駆動部材）４１６
スプール
４１８ スリーブ
４２０ リテーナ10 Casing 26 Input disk 28 Output disk 30 Friction roller 32 Input disk 34 Output disk 36 Friction roller 83 Roller support member 124 Piston 320 Cam 322 Link 410 Speed control valve 412 Step motor 414 Spool with rack (drive member) 416
Spool 418 Sleeve 420 Retainer
Claims (1)
ディスクによって形成されるトロイド状のみぞ内に両デ
ィスクと摩擦接触するように配置される摩擦ローラと、
摩擦ローラを偏心軸を介して回転自在に支持するととも
に両ディスクの軸心に直交する回転軸部を中心として回
動可能かつ上記回転軸部の軸方向に移動可能なローラ支
持部材と、ローラ支持部材を上記回転軸部の軸方向に駆
動可能な油圧シリンダ装置と、を有する摩擦車式無段変
速機の変速制御装置において、油圧シリンダ装置の油圧
を制御する変速制御弁と、ローラ支持部材にこれと一体
に回転するように取り付けられる斜面カムと、カムの斜
面に一端が接触して設けられるとともにカムの回転によ
り揺動可能なリンクと、を有しており、変速制御弁は互
いに相対移動可能な状態にはまり合ったスリーブ及びス
プールと、指令される変速比に応じて回転位置が決定さ
れるステップモータと、ステップモータによって軸方向
に駆動される駆動部材と、を有しており、スプールは駆
動部材と軸方向に一体に移動するように連結され、スリ
ーブは上記回転軸部の回転変位に応じて軸方向に移動す
るように上記リンクの他端と連結され、スリーブ及びス
プールは指令される変速比と上記回転軸部の回転変位と
が対応した状態で両者の相対位置関係が基準状態となっ
て油圧シリンダ装置へ供給する油圧をこれが上記回転軸
部の回転変位を維持するように上記回転軸部に軸方向の
一定の力を作用するように調整し、スリーブとスプール
とが上記基準状態からずれた場合に油圧シリンダ装置へ
供給する油圧を上記回転軸部の回転変位が指令される変
速比に対応するものとなるように上記回転軸部に軸方向
に作用する力を変化させるように調整する構成とされて
いることを特徴とする摩擦車式無段変速機の変速制御装
置。1. An input disk, an output disk, and a friction roller disposed in frictional contact with both disks within a toroidal groove formed by both disks.
a roller support member that rotatably supports a friction roller via an eccentric shaft, is rotatable about a rotation shaft perpendicular to the axes of both disks, and is movable in the axial direction of the rotation shaft; and a roller support member. A hydraulic cylinder device capable of driving a member in the axial direction of the rotating shaft portion, a speed change control device for a friction wheel type continuously variable transmission, comprising a speed change control valve for controlling oil pressure of the hydraulic cylinder device, and a roller support member. It has an inclined cam attached to rotate integrally with the cam, and a link whose one end is in contact with the inclined surface of the cam and can be swung by the rotation of the cam, and the speed change control valve can be moved relative to each other. It has a sleeve and a spool that are fitted in a possible state, a step motor whose rotational position is determined according to a commanded gear ratio, and a drive member that is driven in the axial direction by the step motor. is connected to the drive member so as to move together in the axial direction, the sleeve is connected to the other end of the link so as to move in the axial direction in accordance with the rotational displacement of the rotating shaft portion, and the sleeve and spool are moved according to commands. When the gear ratio corresponds to the rotational displacement of the rotating shaft, the relative positional relationship between the two becomes a reference state, and the hydraulic pressure supplied to the hydraulic cylinder device is adjusted so as to maintain the rotational displacement of the rotating shaft. Adjustment is made so that a constant force in the axial direction is applied to the rotating shaft, and when the sleeve and spool deviate from the reference state, the hydraulic pressure to be supplied to the hydraulic cylinder device is commanded to cause a rotational displacement of the rotating shaft. A speed change control device for a friction wheel type continuously variable transmission, characterized in that it is configured to adjust the force acting on the rotating shaft portion in the axial direction so as to correspond to the speed ratio.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3087821A JP2699687B2 (en) | 1991-03-26 | 1991-03-26 | Transmission control device for friction wheel type continuously variable transmission |
| US07/850,281 US5187995A (en) | 1991-03-26 | 1992-03-12 | Shift control system for continuously variable traction roller transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3087821A JP2699687B2 (en) | 1991-03-26 | 1991-03-26 | Transmission control device for friction wheel type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04296251A true JPH04296251A (en) | 1992-10-20 |
| JP2699687B2 JP2699687B2 (en) | 1998-01-19 |
Family
ID=13925626
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3087821A Expired - Fee Related JP2699687B2 (en) | 1991-03-26 | 1991-03-26 | Transmission control device for friction wheel type continuously variable transmission |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US5187995A (en) |
| JP (1) | JP2699687B2 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04122848U (en) * | 1991-04-23 | 1992-11-05 | 日産自動車株式会社 | Toroidal continuously variable transmission |
| GB9320241D0 (en) * | 1993-10-01 | 1993-11-17 | Greenwood Christopher J | Improvements in or relating to vehicular drivelines including continuously variable-ratio transmissions |
| JP3404973B2 (en) * | 1995-03-29 | 2003-05-12 | 日産自動車株式会社 | Transmission control device for toroidal type continuously variable transmission |
| JP3265908B2 (en) * | 1995-04-24 | 2002-03-18 | 日産自動車株式会社 | Transmission control device for toroidal type continuously variable transmission |
| NL1001279C2 (en) * | 1995-09-25 | 1997-03-26 | Doornes Transmissie Bv | Continuously variable transmission. |
| JP3374677B2 (en) * | 1996-10-31 | 2003-02-10 | 日産自動車株式会社 | Transmission control device for continuously variable transmission |
| JP3636414B2 (en) * | 1997-09-30 | 2005-04-06 | 日産自動車株式会社 | Trunnion support structure of toroidal-type continuously variable transmission |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62121459U (en) * | 1986-01-23 | 1987-08-01 |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61119866A (en) * | 1984-11-15 | 1986-06-07 | Daihatsu Motor Co Ltd | Toroidal type continuously variable transmission |
| JPS61119865A (en) * | 1984-11-15 | 1986-06-07 | Daihatsu Motor Co Ltd | Toroidal type continuously variable transmission |
| JPS61127964A (en) * | 1984-11-27 | 1986-06-16 | Daihatsu Motor Co Ltd | Troidal type continuously variable transmission |
| JPS622061A (en) * | 1985-06-25 | 1987-01-08 | Honda Motor Co Ltd | Friction type continuously variable transmission |
| JPH0672652B2 (en) * | 1986-05-01 | 1994-09-14 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JPS63130954A (en) * | 1986-11-20 | 1988-06-03 | Nissan Motor Co Ltd | Friction wheel type continuously variable transmission |
| JP2715444B2 (en) * | 1988-05-17 | 1998-02-18 | 日産自動車株式会社 | Toroidal continuously variable transmission |
| JPH0772586B2 (en) * | 1988-09-21 | 1995-08-02 | 日産自動車株式会社 | Control device for friction wheel type continuously variable transmission |
| JPH07113410B2 (en) * | 1988-12-16 | 1995-12-06 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JP2734583B2 (en) * | 1988-12-16 | 1998-03-30 | 日産自動車株式会社 | Transmission control device for continuously variable transmission |
| JP2606383B2 (en) * | 1989-08-30 | 1997-04-30 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
| JP2722780B2 (en) * | 1990-05-22 | 1998-03-09 | 日産自動車株式会社 | Friction wheel type continuously variable transmission |
-
1991
- 1991-03-26 JP JP3087821A patent/JP2699687B2/en not_active Expired - Fee Related
-
1992
- 1992-03-12 US US07/850,281 patent/US5187995A/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62121459U (en) * | 1986-01-23 | 1987-08-01 |
Also Published As
| Publication number | Publication date |
|---|---|
| US5187995A (en) | 1993-02-23 |
| JP2699687B2 (en) | 1998-01-19 |
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